CN206530374U - Full hydraulic variable valve mechanism valve stroke control device and internal combustion engine - Google Patents
Full hydraulic variable valve mechanism valve stroke control device and internal combustion engine Download PDFInfo
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- CN206530374U CN206530374U CN201720149159.9U CN201720149159U CN206530374U CN 206530374 U CN206530374 U CN 206530374U CN 201720149159 U CN201720149159 U CN 201720149159U CN 206530374 U CN206530374 U CN 206530374U
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Abstract
The utility model discloses a kind of full hydraulic variable valve mechanism valve stroke control device and internal combustion engine, belong to valve actuating mechanism and the fuel feed system field of internal combustion engine.When the plunger of the valve stroke control device rises to circumferential annular groove and connected with oil leak hole, plunger oil pocket and the hydraulic oil of piston oil intracavitary flow into energy storage chamber by axial straight trough, circumferential annular groove, oil leak hole and the first low pressure oil duct, plunger oil pocket and the reduction of the oil pressure of piston oil intracavitary, oil mass are reduced, and are made the maximum lift of valve and are reduced and fall after rise in advance.The utility model is by controlling the rotational angle of plunger, change the time that circumferential annular groove is connected with oil leak hole, the size of the circumferential annular groove of regulation and the minimum valid circulation area of oil leak hole formation, the hydraulic-oil quantity of control outflow oil leak hole, so as to change the maximum lift of valve and its take a seat the time.The utility model is simple in construction, reliable operation, it is with low cost and suitable for putting on camshaft, underlying and middle internal combustion engine.
Description
Technical field
The utility model is related to valve actuating mechanism and the fuel feed system field of internal combustion engine, particularly relates to a kind of complete variable liquid
Press valve mechanism valve stroke control device and internal combustion engine.
Background technology
Internal combustion engine can realize valve maximum lift, valve duration angle and with gas phase using hydraulic valve system
The continuous variable of position three, this valve system is referred to as full hydraulic variable valve system (Hydraulic Fully
Variable Valve System, abbreviation HFVVS), its energy-saving and emission-reduction to internal combustion engine is significant.At present, with generation
The full hydraulic variable valve system of table has the Uniair systems of Schaeffler company, the electro-hydraulic full changeable air valve of U.S. Ford company
System and Britain Lotus EHFVVT systems etc..The full variable valve system of these hydraulic pressure all employs high-frequency electromagnetic valve conduct
Oil-control switch controls flowing in and out for fluid, and high-frequency electromagnetic valve is present that frequency response speed is low, reliability is low and cost
Expensive deficiency.
Patent No. CN201310296611.0 utility model patent discloses a kind of full hydraulic variable valve of internal combustion engine
The oil-controlling device of system, the device is made up of housing and revolving valve, hydraulic accumulator and the transmission mechanism installed in the housing.Return
Rotary valve is made up of rotary valve key, revolving valve set；Hydraulic accumulator is by energy storage piston, energy-storaging spring, end cap, seal holder ring, rubber
Pad composition, and installed in one end inner chamber of housing；It is energy storage chamber between revolving valve and hydraulic accumulator；Transmission mechanism is by driving cog
Wheel, gear shaft and sliding cross coupling composition, travelling gear are arranged on gear shaft, and gear shaft passes through sliding cross coupling
Being connected with rotary valve key realizes the continuous variable of valve maximum lift, valve duration angle and port timing three.Should
Mechanism is primarily adapted for use in the valve actuating mechanism of camshaft overhead, and for the underlying valve actuating mechanism put with of camshaft, due to hydraulic pressure
The problems such as transmission system is difficult arrangement and longer driving-chain, cause the device be difficult to camshaft is underlying and middle internal combustion engine on
Popularization and application.
Utility model content
The technical problems to be solved in the utility model is to provide a kind of simple in construction, reliable operation, with low cost.Not only fit
For camshaft overhead internal combustion engine, and it is also applied for underlying and middle internal combustion engine the full hydraulic variable valve machine of camshaft
Structure valve stroke control device.
In order to solve the above technical problems, the utility model offer technical scheme is as follows：
A kind of full hydraulic variable valve mechanism valve stroke control device, including the housing of high-pressure oil duct is provided with, it is described
Be provided with housing for be connected to Engine Cam drive component hydraulic plunger type oil-controlling device, for being connected to internal combustion engine
The piston type pneumatic door drive of valve assembly, the hydraulic accumulating device for connecting I. C. engine oil lubricating system and entrance list
To valve, wherein：
The hydraulic plunger type oil-controlling device includes setting plunger bushing on the housing, the endoporus with the plunger bushing
The plunger governor motion of the plunger that is engaged, the plunger spring for making the plunger return and the regulation plunger rotation angle,
The plunger includes the plunger core being engaged with the plunger bushing and the plunger rod for being arranged at the plunger core lower end, the plunger
Formed between the top of core and the plunger bushing on the plunger oil pocket connected with the high-pressure oil duct, the face of cylinder of the plunger core
It is provided with the axial straight trough connected with the plunger oil pocket and the circumferential annular groove connected with the axial straight trough, the plunger bushing
Side wall on be provided with oil leak hole；
The piston type pneumatic door drive includes hydraulic piston, the piston bush matched with hydraulic piston, the hydraulic pressure
The piston oil pocket connected with the high-pressure oil duct is formed between the top of piston and the piston bush；
The hydraulic accumulating device include setting hydraulic accumulator on the housing and by the accumulator with it is described
The energy storage chamber that housing is constituted, be provided with the housing energy storage chamber is connected with oil leak hole the first low pressure oil duct, by institute
State energy storage chamber the second low pressure oil duct connected with high-pressure oil duct and connect the energy storage chamber with I. C. engine oil lubricating system
3rd low pressure oil duct, the energy storage chamber can by the first low pressure oil duct, oil leak hole, circumferential annular groove and axial straight trough with
The plunger oil pocket connection；
The inlet one-way valve is arranged between the high-pressure oil duct and the second low pressure oil duct.
Further, distance of the top edge away from plunger top of the circumferential annular groove is justified since axial straight trough along plunger
Circumferential direction gradually increases or constant, and the depth of the circumferential annular groove gradually subtracts since axial straight trough along plunger circumferencial direction
It is small；
Or, distance of the top edge away from plunger top of the circumferential annular groove is since axial straight trough along plunger circumference side
To gradually increasing, the depth of the circumferential annular groove is constant.
Further, the full depth or partial depth of the circumferential annular groove are not more than the four of the diameter of the oil leak hole
/ mono-.
Further, the cross section of the circumferential annular groove is triangle, circular arc, trapezoidal or rectangle.
Further, the plunger governor motion includes the control set coordinated with the cylindrical gap in bottom of the plunger bushing
Cylinder, the end of the control sleeve is provided with guide groove, and the bottom of the plunger rod is provided with what is be engaged with the guide groove
Joint tongue.
Further, the plunger governor motion also include motor or proportion electro-magnet, the control sleeve it is cylindrical on
Gear ring is provided with, motor or the proportion electro-magnet drive connection has the rack or gear being meshed with the gear ring.
Further, it is provided with the unidirectional hole connected respectively with the high-pressure oil duct on the piston type pneumatic door drive
And throttle orifice, be provided with plunger shaft check valve in the unidirectional hole, the plunger shaft pass through the unidirectional hole and throttle orifice with it is high
Road connection is pressed oil, when valve assembly is closed, the top of the hydraulic piston is located at the top of the throttle orifice.
Further, the hydraulic accumulator includes being fixedly mounted end cap and the body clearance on the housing
The energy storage piston of cooperation and the accumulator spring being arranged between the end cap and energy storage piston.
A kind of internal combustion engine, including above-mentioned full hydraulic variable valve mechanism valve stroke control device.
When full hydraulic variable valve mechanism valve stroke control device and internal combustion engine of the present utility model, actuated by cams
The bent axle of distribution cam axle and internal combustion engine in component (including distribution cam axle, tappet and tappet) is together operated, valve cam
Driving tappet and tappet simultaneously make the plunger of hydraulic plunger type oil-controlling device do linear reciprocating motion with plunger spring collective effect,
I.e.：When valve cam is in the ascent stage, cam jack-up plunger makes plunger move upwards；When cam is in descending branch, plunger
(moving downward) is resetted in the presence of plunger spring.Plunger is in upward stroke, the post in hydraulic plunger type oil-controlling device
The volume for filling in oil pocket reduces so that the oil pressure rise in high-pressure oil duct, the hydraulic oil of high-pressure oil duct flows into piston oil pocket, promotes and live
The hydraulic piston of plug valve actuator overcomes the active force of valve spring to open valve；When plunger rises to circumferential annular
When groove is connected with oil leak hole, hydraulic oil in high-pressure oil duct by plunger oil pocket, axial straight trough, circumferential annular groove, oil leak hole and
First low pressure oil duct flows into energy storage chamber, and interior and piston oil intracavitary the oil mass of Plunger oil intracavitary, high-pressure oil duct is reduced, oil pressure reduction,
Valve maximum lift is reduced；Plunger is in descending stroke, when circumferential annular groove and oil leak hole, which disconnect, to be connected, energy storage chamber and high pressure
Oil duct namely disconnection connection, valve is as the decline of plunger gradually falls after rise and finally takes a seat.
When internal combustion engine is in medium and small load operation, it is necessary to which the maximum lift of valve diminishes, and valve-closing time is more early,
The rotational angle of the plunger governor motion pilot plunger of hydraulic plunger type oil-controlling device causes circumferential annular groove close to axial straight trough
Part connected with oil leak hole, the time for making circumferential annular groove be connected with oil leak hole is longer, and circumferential annular groove and oil leak hole shape
Into minimum valid circulation area it is larger, cause Plunger oil intracavitary by oil leak hole flow into energy storage chamber oil mass it is more, finally make
The maximum lift of valve reduces and closed Before Bottom Dead Center.When internal combustion engine is in compared with large load operation, now need larger
Valve stroke, and valve-closing time is later, the angle of rotation of the plunger governor motion pilot plunger of hydraulic plunger type oil-controlling device
Degree causes part of the circumferential annular groove away from axial straight trough to be connected with oil leak hole, the time for making circumferential annular groove be connected with oil leak hole
Shorter, the minimum valid circulation area of circumferential annular groove and oil leak hole formation is smaller, causes Plunger oil intracavitary to pass through oil leak hole stream
The oil mass for entering energy storage chamber is less, finally makes the maximum lift of valve larger and is closed near lower dead center.When internal combustion engine is in height
, it is necessary to which valve is fully opened during fast full load mode operation, and there is larger air inlet retard angle, then plunger governor motion passes through
The rotational angle of pilot plunger causes least significant end of the circumferential annular groove away from axial straight trough to be connected with oil leak hole, or even makes circumferential ring
Shape groove disconnects all the time with oil leak hole, and the oil mass that Plunger oil intracavitary flows into energy storage chamber by oil leak hole is seldom even equal to 0, now gas
Door lift depends on Valve-train Cam, and valve has maximum lift and larger air inlet retard angle.
When valve-closing, if corresponding valve cam is still in the process of decline, with the decline of plunger, Plunger oil
When the pressure of hydraulic oil decreases below the pressure of energy storage chamber in the volume increase of chamber, high-pressure oil duct, energy storage chamber passes through entrance list
Hydraulic oil is supplemented into high-pressure oil duct to valve, it is ensured that hydraulic oil is full of plunger oil pocket, piston oil pocket and high-pressure oil duct all the time.
Plunger bushing and piston bush in full hydraulic variable valve mechanism valve stroke control device of the present utility model are fixed
Install in the housing, reduce the leakage rate of fluid, adopted only between plunger core and plunger bushing, between hydraulic piston and piston bush
With clearance seal, so as to drastically increase the control accuracy of valve stroke.In addition full hydraulic variable valve of the present utility model
Hydraulic oil in mechanism valve stroke control device is all using the machine oil in lubricating system of IC engine.
In summary, compared with prior art, the utility model has the advantages that：
(1) the minimum valid circulation area that the oil leak hole on the circumferential annular groove and plunger bushing in plunger core is formed can be obtained
To accurate control, the time that circumferential annular groove is connected with oil leak hole can also accurately be adjusted, can accurately be controlled from draining
The oil mass of hole outflow, makes the continuous variable of valve maximum lift, valve duration angle and close moment three.
(2) by the time for controlling circumferential annular groove to be connected with oil leak hole, and circumferential annular groove is adjusted and oil leak hole is formed
Minimum valid circulation area size, can not only accurately control the oil mass flowed out from oil leak hole, and it can be controlled to flow
Speed, is easy to accurately control valve stroke and its characteristics of motion, meets the demand of full hydraulic variable valve mechanism dynamic performance.
(3) put on full hydraulic variable valve mechanism valve stroke control device of the present utility model and camshaft, in put and
Underlying internal combustion engine all has good matching, using in traditional combustion engine, and the change of former machine is smaller and IC engine airframe
Etc. main parts size without change.
(4) compared with external existing advanced technology, save high-frequency electromagnetic valve, thus with simple in construction, reliable operation,
Advantage with low cost.
Brief description of the drawings
Fig. 1 is the structural representation of full hydraulic variable valve mechanism valve stroke control device of the present utility model；
Fig. 2 is hydraulic plunger type oil-control dress in full hydraulic variable valve mechanism valve stroke control device of the present utility model
The structural representation put；
The sectional view that Fig. 3 is A-A in Fig. 2；
Fig. 4 is oil leak hole and the partial structural diagram of circumferential annular groove；
Fig. 5 is the embodiment 1 of plunger in full hydraulic variable valve mechanism valve stroke control device of the present utility model
Structural representation；
Fig. 6 is the embodiment 2 of plunger in full hydraulic variable valve mechanism valve stroke control device of the present utility model
Structural representation；
Fig. 7 is the embodiment 3 of plunger in full hydraulic variable valve mechanism valve stroke control device of the present utility model
Structural representation；
Fig. 8 is the embodiment 4 of plunger in full hydraulic variable valve mechanism valve stroke control device of the present utility model
Structural representation；
Fig. 9 is the embodiment 5 of plunger in full hydraulic variable valve mechanism valve stroke control device of the present utility model
Structural representation；
Figure 10 is the valve liter under the control of full hydraulic variable valve mechanism valve stroke control device of the present utility model
The change curve of journey.
Embodiment
To make the technical problems to be solved in the utility model, technical scheme and advantage clearer, below in conjunction with accompanying drawing
And specific embodiment is described in detail.
On the one hand, the utility model provides a kind of full hydraulic variable valve mechanism valve stroke control device, such as Fig. 1 to figure
Shown in 10, including it is provided with high-pressure oil duct 1-1 housing 1, housing 1 and is provided with for being connected to Engine Cam drive component
7 hydraulic plunger type oil-controlling device 3, the piston type pneumatic door drive 5 for being connected to engine valve component 8, for even
The hydraulic accumulating device 4 and inlet one-way valve 2 of logical I. C. engine oil lubricating system, wherein：
Hydraulic plunger type oil-controlling device 3 includes the plunger bushing 3-1 being arranged on housing 1 and plunger bushing 3-1 endoporus matches
The plunger 3-2 of conjunction, make plunger 3-2 reset plunger spring 3-4 and pilot plunger 3-2 circumferentially rotate angle plunger regulation machine
Structure 3-3, plunger 3-2 include the plunger core 3-2-1 being engaged with plunger bushing 3-1 and the plunger for being arranged at plunger core 3-2-1 lower ends
The plunger oil pocket 3-5 connected with high-pressure oil duct 1-1, post are formed between bar 3-2-2, plunger core 3-2-1 top and plunger bushing 3-1
Be provided with the plug core 3-2-1 face of cylinder the axial straight trough 3-2-1-2 that is connected with plunger oil pocket 3-5 and with axial straight trough 3-2-1-
Oil leak hole 3-1-1 is provided with the circumferential annular groove 3-2-1-1 of 2 connections, plunger bushing 3-1 side wall；
Piston type pneumatic door drive 5 includes hydraulic piston 5-1, the piston bush 5-2 matched with hydraulic piston 5-1, liquid
The piston oil pocket 5-4 connected with high-pressure oil duct 1-1 is formed between pressure piston 5-1 top and piston bush 5-2；
Hydraulic accumulating device includes the hydraulic accumulator 4 being arranged on housing 1 and is made up of hydraulic accumulator 4 with housing 1
Energy storage chamber 9, the first low pressure oil duct 1-2 for connecting energy storage chamber 9 with oil leak hole 3-1-1 is provided with housing 1, by energy storage chamber 9
The second low pressure oil duct 1-3 for being connected with high-pressure oil duct 1-1 and the by energy storage chamber 9 and the oil lubricating system connectivity of internal combustion engine the 3rd
Low pressure oil duct 1-4, energy storage chamber 9 can pass through the first low pressure oil duct 1-2, oil leak hole 3-1-1, circumference annular groove 3-2-1-1 and axle
Connected to straight trough 3-2-1-2 with plunger oil pocket 3-5；
Inlet one-way valve 2 is arranged between high-pressure oil duct 1-1 and the second low pressure oil duct 1-3.
During full hydraulic variable valve mechanism valve stroke control device work of the present utility model, (the bag of actuated by cams component 7
Include valve cam, tappet and tappet) in valve cam and the bent axle of internal combustion engine together operate, valve cam driving tappet and very
Bar simultaneously makes the plunger 3-2 of hydraulic plunger type oil-controlling device 3 do linear reciprocating motion with plunger spring 3-4 collective effects, i.e.,：When convex
When wheel is in the ascent stage, cam jack-up plunger 3-2 makes plunger 3-2 move upwards；When cam is in descending branch, plunger 3-2 exists
(moving downward) is resetted in the presence of plunger spring 3-4.Plunger 3-2 is in upward stroke, in hydraulic plunger type oil-controlling device 3
Plunger oil pocket 3-5 volume reduce so that the rise of oil pressure in high-pressure oil duct 1-1, high-pressure oil duct 1-1 hydraulic oil is through making a living
Flow into piston oil pocket 5-4 in plug valve actuator 5, promote hydraulic piston 5-2 to overcome the active force of valve spring by gas
Door is opened；When plunger 3-2, which rises to circumferential annular groove 3-2-1-1, to be connected with oil leak hole 3-1-1, plunger oil pocket 3-5 and piston
Hydraulic oil in oil pocket 5-4 passes through axial straight trough 3-2-1-2, circumferential annular groove 3-2-1-1, oil leak hole 3-1-1 and the first low pressure
Oil duct 1-2 flows into energy storage chamber 9, reduces the oil mass in plunger oil pocket 3-5 and piston oil pocket 5-4, oil pressure is reduced, and causes valve most
High-lift is reduced and fallen after rise in advance；Plunger 3-2 is in descending stroke, when circumferential annular groove 3-2-1-1 and oil leak hole 3-1-1 disconnects
During connection, energy storage chamber 9 is connected with high-pressure oil duct 1-1 namely disconnection, and valve is as plunger 3-2 decline gradually falls after rise and finally falls
Seat.
When internal combustion engine is in medium and small load operation, it is necessary to which the maximum lift of valve diminishes, and valve-closing time is more early,
The plunger governor motion 3-3 pilot plungers 3-2 of hydraulic plunger type oil-controlling device 3 rotational angle causes circumferential annular groove 3-2-1-
1 connects close to axial straight trough 3-2-1-2 part with oil leak hole 3-1-1, makes circumferential annular groove 3-2-1-1 and oil leak hole 3-1-1
The time of connection is longer, and oil leak hole 3-1-1 and the minimum valid circulation area of circumferential annular groove 3-2-1-1 formation are larger, cause
Oil mass in plunger oil pocket 3-5 and piston oil pocket 5-4 by oil leak hole 3-1-1 inflow energy storage chambers 9 is more, finally makes valve most
High-lift is obviously reduced and closed Before Bottom Dead Center, curve C and D in such as Figure 10.When internal combustion engine is in compared with large load operation,
Larger valve stroke is now needed, and valve-closing time is later, then plunger governor motion 3-3 pilot plungers 3-2 rotation
Angle causes parts of the circumferential annular groove 3-2-1-1 away from axial straight trough 3-2-1-2 to be connected with oil leak hole 3-1-1, makes circumferential ring
Time that shape groove 3-2-1-1 is connected with oil leak hole 3-1-1 is shorter, oil leak hole 3-1-1 with circumferential annular groove 3-2-1-1 formation most
Small valid circulation area is smaller, causes the oil mass for flowing into energy storage chamber 9 in plunger oil pocket 3-5 and piston oil pocket 5-4 by oil leak hole
It is less, the maximum lift of valve has been reduced and has been closed after lower dead center, the curve B in such as Figure 10.Work as internal combustion engine
, it is necessary to which valve is fully opened when being run in high speed full load, and there is larger air inlet retard angle, then plunger governor motion 3-
3 by pilot plunger 3-2 rotational angle cause least significant ends of the circumferential annular groove 3-2-1-1 away from axial straight trough 3-2-1-2 with
Oil leak hole 3-1-1 is connected, or even circumferential annular groove 3-2-1-1 and oil leak hole 3-1-1 is disconnected all the time, plunger oil pocket 3-5 and work
The oil mass seldom even equal to 0 for flowing into energy storage chamber 9 in oil pocket 5-4 by oil leak hole 3-1-1 is filled in, now valve stroke depends on matching somebody with somebody
The molded line of gas cam, valve has the curve A in maximum lift and larger air inlet retard angle, such as Figure 10.
When valve-closing, if corresponding valve cam is still in the process of decline, with plunger 3-2 decline, post
When the pressure for filling in hydraulic oil in oil pocket 3-5 volume increase, high-pressure oil duct 1-1 decreases below the pressure of energy storage chamber 9, energy storage chamber
9 supplement hydraulic oil by inlet one-way valve 2 into high-pressure oil duct 1-1, it is ensured that hydraulic oil is full of plunger oil pocket 3-5, piston all the time
Oil pocket 5-4 and high-pressure oil duct 1-1.
To sum up, the utility model has the advantages that：
(1) the minimum valid circulation area that the oil leak hole on the circumferential annular groove and plunger bushing in plunger core is formed can be obtained
To accurate control, the time that circumferential annular groove 3-2-1-1 is connected with oil leak hole 3-1-1 can also accurately be adjusted, Neng Gouzhun
The oil mass that really control is flowed out from oil leak hole, makes valve maximum lift, valve duration angle and the continuous of close moment three can
Become.
(2) by the time for controlling circumference annular groove 3-2-1-1 to be connected with oil leak hole 3-1-1, and circumferential annular groove is adjusted
The size of the minimum valid circulation area of 3-2-1-1 and oil leak hole 3-1-1 formation, can accurately control hydraulic oil to flow out oil leak hole
3-1-1 flow velocity, is easy to accurately control valve stroke and its characteristics of motion, meets full hydraulic variable valve mechanism dynamic performance
Demand.
(3) put on full hydraulic variable valve mechanism valve stroke control device of the present utility model and camshaft, in put and
Underlying internal combustion engine all has good matching, using in traditional combustion engine, and the change of former machine is smaller and key components and parts
Without change.
(4) compared with external existing advanced technology, save high-frequency electromagnetic valve, thus with simple in construction, reliable operation,
Advantage with low cost,
(5) a set of valve stroke control device controls a cylinder, it is adaptable to single cylinder and multi-cylinder engine, expands and entirely may be used
Become the scope of application of hydraulic valve mechanism.
It will be appreciated by persons skilled in the art that be previously mentioned high pressure in the utility model and low pressure be both comparatively
, do not limit to when pressure must reach certain numerical value and be just referred to as high pressure or low pressure.
In the utility model, housing both can be a single part, can also divide housing 135 into two parts (housing 1
With top cover 6) process respectively, then both are fixedly connected, now, high-pressure oil duct 1-1 is arranged on top cover 6.
Circumferential annular groove 3-2-1-1 several concrete structures are given below：
Embodiment 1
As shown in figure 5, circumferential annular groove 3-2-1-1 distance of the top edge away from plunger 3-2 tops is from axial straight trough 3-2-
1-2 starts gradually to increase along plunger 3-2 circumferencial directions, and circumferential annular groove 3-2-1-1 depth is since axial straight trough 3-2-1-2
It is gradually reduced along plunger 3-2 circumferencial directions, circumferential annular groove 3-2-1-1 cross section is triangle.
In the present embodiment, when the valve maximum lift of needs diminishes, and valve-closing time it is more early when, plunger governor motion
3-3 pilot plunger 3-2 rotational angles cause circumferential annular groove 3-2-1-1 close to axial straight trough 3-2-1-2 part and oil leak hole
3-1-1 is connected, because circumferential annular groove 3-2-1-1 this portion upper edge is away from the in small distance of plunger 3-2 tops, and circumferentially
Annular groove 3-2-1-1 depth is deeper so that the time that circumferential annular groove 3-2-1-1 is connected with oil leak hole 3-1-1 is elongated, circumferential
The minimum valid circulation area that annular groove 3-2-1-1 and oil leak hole 3-1-1 is formed is larger, causes plunger oil pocket 3-5 and piston oil
The oil mass that hydraulic oil in chamber 5-4 flows into energy storage chamber 9 by oil leak hole 3-1-1 is more, finally makes the maximum lift of valve obvious
Reduce and close Before Bottom Dead Center, curve C and D in such as Figure 10.Similarly, when the valve maximum lift of needs is larger, and valve
When shut-in time is later, then plunger governor motion 3-3 pilot plungers 3-2 rotational angle make it that circumferential annular groove 3-2-1-1 is remote
Connected off axis to straight trough 3-2-1-2 part with oil leak hole 3-1-1, due to circumferential annular groove 3-2-1-1 this portion upper edge
Away from the in larger distance of plunger 3-2 tops, and this partially circumferentially annular groove 3-2-1-1 depth it is shallower so that circumferential annular groove 3-
2-1-1 shortens with the oil leak hole 3-1-1 times connected, and the minimum of circumferential annular groove 3-2-1-1 and oil leak hole 3-1-1 formation is effectively
Circulation area is smaller, cause in plunger oil pocket 3-5 and piston oil pocket 5-4 by oil leak hole 3-5 flow into the oil mass of energy storage chamber 9 compared with
It is few, the maximum lift of valve has been reduced and has been closed after lower dead center, the curve B in such as Figure 10.When needing valve complete
Open, and during with larger air inlet retard angle, then plunger governor motion 3-3 is caused by pilot plunger 3-2 rotational angle
Circumferential annular groove 3-2-1-1 is connected, or even make circumferential annular off axis to end farthest straight trough 3-2-1-2 with oil leak hole 3-1-1
Groove 3-2-1-1 is disconnected all the time with oil leak hole 3-1-1, and the oil mass of energy storage chamber 9 is flowed into very by oil leak hole -1-1 in plunger oil pocket 3-5
0 is even equal to less, now valve stroke depends on the molded line of valve cam, valve is slow with maximum lift and larger air inlet
The curve A closed in angle, such as Figure 10.
Embodiment 2
As shown in fig. 6, circumferential annular groove 3-2-1-1 cross section is circular arc, remaining structure is same as Example 1.
Embodiment 3
As shown in fig. 7, circumferential annular groove 3-2-1-1 distance of the top edge away from plunger 3-2 tops is from axial straight trough 3-2-
1-2 starts gradually to increase along plunger 3-2 circumferencial directions, and distance of the lower edge away from plunger 3-2 tops is opened from axial straight trough 3-2-1-2
Begin constant along plunger 3-2 circumferencial directions, circumferential annular groove 3-2-1-1 depth is constant.When plunger governor motion 3-3 pilot plungers
3-2 rotates different angles, when, circumferential annular groove 3-2-1-1 is different at the time of connection from oil leak hole 3-1-1 so that Plunger oil
Also respective change at the time of flowing into energy storage chamber 9 by oil leak hole 3-1-1 in chamber 3-5 and piston oil pocket 5-4, causes the maximum of valve
Lift also changes therewith.
Embodiment 4
As shown in figure 8, circumferential annular groove 3-2-1-1 top edge and lower edges parallel, and away from plunger 3-2 tops away from
Gradually increase along plunger 3-2 circumferencial directions from since axial straight trough 3-2-1-2, circumferential annular groove 3-2-1-1 depth is not
Become.
Embodiment 5
As shown in figure 9, circumferential annular groove 3-2-1-1 top edge and lower edges parallel, and away from plunger 3-2 tops away from
Constant along plunger 3-2 circumferencial directions from since axial straight trough 3-2-1-2, circumferential annular groove 3-2-1-1 depth is from axial direction
Straight trough 3-2-1-2 starts to be gradually reduced along plunger 3-2 circumferencial directions, and circumferential annular groove 3-2-1-1 cross section is rectangle.
In above-mentioned 5 embodiments, circumferential annular groove 3-2-1-1 shape of cross section except for triangle, circular arc or
Outside rectangle, can also be trapezoidal or those skilled in the art it is conceivable that the other shapes for meeting mentioned above principle, do not influence
The realization of technical solutions of the utility model.Circumferential annular groove 3-2-1-1 shape of cross section refers to that circumferential annular groove 3-2-1-1 exists
The notch geometry formed by the longitudinal cross-section of plunger core 3-2-1 center line.
According to fluid mechanics knowledge, in the case where not considering other factors, when fluid is by the larger circumference in cross section
When annular groove 3-2-1-1 flows into the less oil leak hole 3-1-1 in cross section, as shown in figure 4, the flow of fluid and oil leak hole 3-1-1
The lateral area formed between circumferential annular groove 3-2-1-1 is relevant.When between oil leak hole 3-1-1 and circumferential annular groove 3-2-1-1
The lateral area of formation is more than or equal to oil leak hole 3-1-1 cross-sectional area, i.e. oil leak hole 3-1-1 and circumferential annular groove 3-2-1-1 it
Between apart from h be more than or equal to oil leak hole 3-1-1 diameter a quarter when, the flow of fluid is by the transversal of oil leak hole 3-1-1
Area is determined；When the lateral area formed between oil leak hole 3-1-1 and circumferential annular groove 3-2-1-1 is less than oil leak hole 3-1-1 horizontal stroke
The distance between sectional area, i.e. oil leak hole 3-1-1 and circumferential annular groove 3-2-1-1 h are less than four points of oil leak hole 3-1-1 diameter
For the moment, the flow of fluid is determined by the distance between oil leak hole 3-1-1 and circumferential annular groove 3-2-1-1 h.
In the utility model, circumferential annular groove 3-2-1-1 full depth or partial depth are preferably not greater than draining
The a quarter of hole 3-1-1 diameter.Now, hydraulic oil is by high-pressure oil duct 1-1, plunger oil pocket 3-5, axial straight trough 3-2-1-
2nd, the flow that circumferential annular groove 3-2-1-1, oil leak hole 3-1-1 and the first low pressure oil duct 1-2 are back in energy storage chamber 9 is obtained rationally
Control, the fall velocity of valve namely obtains slow control, curve B3 as shown in Figure 9, C3 sections of curve, and valve then will not be along along Fig. 9
Curve C3 ' sections drastically fall after rise, the company of valve maximum lift, valve duration angle and close moment three can not only be realized
It is continuous variable, and can ensure that lift, speed and the accelerating curve change of valve motion are more gentle, be not in larger
Rise and fall, so as to meet internal combustion engine to the demand in terms of valve mechanism dynamic performance.
Further, as shown in Figures 2 and 3, plunger governor motion 3-3 includes the cylindrical gap in bottom with plunger bushing 3-1
The control sleeve 3-3-1 of cooperation, control sleeve 3-3-1 end are preferably provided with guide groove 3-3-1-2, plunger rod 3-2-2's
Bottom is provided with the joint tongue 3-2-2-2 being engaged with guide groove 3-3-1-2.The utility model is by joint tongue 3-2-2-2 with being oriented to
Groove 3-3-1-2 cooperation causes plunger 3-2 to do linear reciprocating motion relative to plunger bushing 3-1, can turn again around central shaft
Dynamic, this structure can enable plunger bushing 3-1 to be fixedly mounted in housing 1, it is to avoid plunger bushing 3-1 is because relative to housing
1 rotates and fit clearance between housing 1 is larger causes oil leak.
In addition, as shown in Figure 1 to Figure 3, plunger governor motion 3-3 can also include motor or proportion electro-magnet (does not show
Go out), control sleeve 3-3-1 it is cylindrical on be provided with the gear ring 3-3-1-1 engaged with rack 3-3-2, motor or proportion electro-magnet
Drive connection has the rack 3-3-2 being meshed with gear ring 3-3-1-1.Using when, rack 3-3-2 is by stepper motor or ratio electromagnetism
Sheet iron strip is moved.Judge the optimal lift of valve according to engine conditions and open the duration, by controlling stepper motor or ratio electricity
Magnet pulls rack 3-3-2 pilot plungers 3-2 rotational angle, changes circumference annular groove 3-2-1-1 and oil leak hole 3-1-1 phase
To position, the draining start time and draining duration of hydraulic oil in plunger oil pocket 3-5 are controlled, so as to realize that valve most rises higher
The continuous variable of journey, valve duration angle and close moment three.When plunger 3-2 is in distribution cam axle, actuated by cams component 7
During with carrying out linear reciprocating motion under plunger spring 3-4 collective effect, joint tongue 3-2-2-2 can leading in guide groove 3-3-1-2
Moved up and down to effect is lower；When motor or proportion electro-magnet pull rack 3-3-2 motions, because guide groove 3-3-1-2 is to tenon
Tongue 3-2-3 restriction effect so that plunger 3-2 is rotated with control sleeve 3-3-1 around plunger 3-2 center line, so as to realize
The change of circumferential annular groove 3-2-1-1 and oil leak hole 3-1-1 relative position.
In addition, plunger governor motion 3-3 is except that can use the gear ring 3-3- on rack 3-3-2 and control sleeve 3-3-1
1-1 is meshed outer, it would however also be possible to employ gear is engaged transmission with gear ring 3-3-1-1.Gear drive is steady, can with work
Lean on, efficiency high and the features such as long lifespan.It is of course also possible to use the kind of drive pilot plunger such as worm and gear 3-2 angle of rotation
Degree.
It is preferred that, plunger rod 3-2-2 end can be provided with hemispherical groove 3-2-2-1 (as shown in Figure 7 and Figure 8) or
Person's hemispherical projections.When the top of camshaft actuated component 7 is hemispherical projections, plunger rod 3-2-2 end be then with it is convex
The hemispherical groove that the hemispherical projections of wheel shaft drive component 7 are engaged；When the top of camshaft actuated component 7 is recessed for hemispherical
During groove, plunger rod 3-2-2 end is then the hemispherical projections being engaged with the hemispherical projections of camshaft actuated component 7.It is convex
By this universal connection between wheel shaft drive component 7 and plunger rod 3-2-2, it can be adjusted between plunger rod 3-2-2
Angle, it is ensured that plunger 3-2 remains linear reciprocating motion when rack 3-3-2 is motionless.
When plunger rod 3-2-2 end is planar structure or roller structure, camshaft actuated component 7 can be omitted so that matching somebody with somebody
The direct drive plunger 3-2 motions of gas camshaft.
As another improvement of the present utility model, as shown in figure 1, being preferably provided with piston type pneumatic door drive 5
The unidirectional hole 5-2-2 and throttle orifice 5-2-1 connected respectively with high-pressure oil duct 1-1.It is unidirectional that plunger shaft is provided with unidirectional hole 5-2-2
Valve 5-3, plunger shaft 5-4 are connected by unidirectional hole 5-2-2 and throttle orifice 5-2-1 with high-pressure oil duct 1-1.When valve assembly is closed
When, hydraulic piston 5-1 top is located at throttle orifice 5-2-1 top.Valve assembly 8 is after closing, and hydraulic piston 5-1 will throttle
Hole 5-2-1 is sealed.When valve cam drives plunger 3-2 in upward stroke, plunger oil pocket 3-5 volume reduces so that high pressure
The pressure rise of hydraulic oil in oil duct 1-1, high-pressure oil duct 1-1 hydraulic oil passes through unidirectional hole 5-2-2 and plunger shaft check valve
5-3 flows into plunger shaft 5-4, promotes hydraulic piston 5-1 to overcome the active force of valve spring to open valve；With hydraulic piston 5-
1 is moved downward, and throttle orifice 5-2-1 and hydraulic piston 5-1 contact area are gradually reduced, throttle orifice 5-2-1 and plunger shaft 5-4
Connection area gradually increase, then the hydraulic oil in high-pressure oil duct 1-1 by throttle orifice 5-2-1 flow into plunger shaft 5-4, improve
Hydraulic piston 5-1 promotes the opening speed of valve assembly.When valve is falling after rise in the presence of valve spring, due to plunger shaft list
To valve 5-3 effect, the hydraulic oil in plunger shaft 5-4 can not flow into high-pressure oil duct 1-1 from unidirectional hole 5-2-2, can only be from throttling
Hole 5-2-1 flows into high-pressure oil duct 1-1.When valve is fallen back to so that the hydraulic piston 5-1 face of cylinder is contacted with throttle orifice 5-2-1
When, with the increase of hydraulic piston 5-1 and throttle orifice 5-2-1 contact area, throttle orifice 5-2-1 minimum valid circulation area
Reduce, the flow of hydraulic oil is gradually reduced in plunger shaft 5-4, and pressure gradually increases, then the seating velocity of valve is gradually reduced, most
Steadily take a seat afterwards.
In the utility model, plunger shaft check valve 5-3 is arranged between hydraulic piston 5-1 and hydraulic piston set 5-2, in order to
Avoid increasing hydraulic piston 5-1 because installing plunger shaft check valve 5-3 and hydraulic piston covers 5-2 physical dimension, hydraulic piston
5-1 top can set it is fluted with increase plunger shaft check valve 5-3 installing space and meet plunger shaft 5-4 volume will
Ask.
In the course of normal operation of internal combustion engine, because the hydraulic oil in high-pressure oil duct 1-1 is flowed to by oil leak hole 3-1-1
The oil lubricating system of internal combustion engine, causes the fluctuation of oil pressure in oil lubricating system.In order to maintain the oil in oil lubricating system
The stability of pressure, as shown in figure 1, hydraulic accumulator 4 is preferably included between the end cap 4-3 being fixedly mounted on housing 1 and housing 1
The energy storage piston 4-1 of the gap cooperation and accumulator spring 4-2 being arranged between end cap 4-3 and energy storage piston 4-1, energy storage piston
Energy storage chamber 9 is formed between 4-1 and housing 1.When the oil pressure increase in oil lubricating system, energy storage piston 4-1 is in hydraulic oil
Accumulator spring 4-2 active force is overcome to press to end cap 4-3 under effect；When the oil pressure reduction in oil lubricating system, accumulation of energy
Piston 4-1 remote end cap 4-3 in the presence of accumulator spring 4-2, to maintain the stability of the oil pressure in oil lubricating system.
On the other hand, the utility model provides a kind of internal combustion engine, including above-mentioned full hydraulic variable valve mechanism valve stroke
Control device, structure with it is upper identical, here is omitted.
During internal combustion engine of the present utility model, matching somebody with somebody in actuated by cams component 7 (including valve cam, tappet and tappet)
The bent axle of gas cam and internal combustion engine is together operated, and valve cam drives tappet and tappet and made with plunger spring 3-4 collective effects
The plunger 3-2 of hydraulic plunger type oil-controlling device 3 does linear reciprocating motion, i.e.,：When cam is in the ascent stage, cam jack-up plunger
3-2 makes plunger 3-2 move upwards；When cam be in descending branch when, plunger 3-2 resetted in the presence of plunger spring 3-4 (i.e. to
Lower motion).Plunger 3-2 is in upward stroke, and the volume of the plunger oil pocket 3-5 in hydraulic plunger type oil-controlling device 3 reduces so that
Oil pressure rise in high-pressure oil duct 1-1, high-pressure oil duct 1-1 hydraulic oil is by flowing into piston in piston type pneumatic door drive 5
In oil pocket 5-4, hydraulic piston 5-2 is promoted to overcome the active force of valve spring to open valve；When plunger 3-2 rises to circumferential ring
When shape groove 3-2-1-1 is connected with oil leak hole 3-1-1, the hydraulic oil in plunger oil pocket 3-5 and piston oil pocket 5-4 passes through axial straight trough
3-2-1-2, circumferential annular groove 3-2-1-1, oil leak hole 3-1-1 and the first low pressure oil duct 1-2 flow into energy storage chamber 9, make plunger oil pocket
Oil mass in 3-5 and piston oil pocket 5-4 is reduced, oil pressure reduction, causes valve maximum lift to reduce and fall after rise in advance；Plunger 3-2
In descending stroke, when circumferential annular groove 3-2-1-1 and oil leak hole 3-1-1, which disconnect, to be connected, energy storage chamber 9 and high-pressure oil duct 1-1
Namely connection is disconnected, valve is as plunger 3-2 decline gradually falls after rise and finally takes a seat.
When internal combustion engine is in medium and small load operation, it is necessary to which the maximum lift of valve diminishes, and valve-closing time is more early,
The plunger governor motion 3-3 pilot plungers 3-2 of hydraulic plunger type oil-controlling device 3 rotational angle causes circumferential annular groove 3-2-1-
1 connects close to axial straight trough 3-2-1-2 part with oil leak hole 3-1-1, makes circumferential annular groove 3-2-1-1 and oil leak hole 3-1-1
The time of connection is longer, and oil leak hole 3-1-1 and the minimum valid circulation area of circumferential annular groove 3-2-1-1 formation are larger, cause
Oil mass in plunger oil pocket 3-5 and piston oil pocket 5-4 by oil leak hole 3-1-1 inflow energy storage chambers 9 is more, finally makes valve most
High-lift is obviously reduced and closed Before Bottom Dead Center, curve C and D in such as Figure 10.When internal combustion engine is in compared with large load operation,
Larger valve stroke is now needed, and valve-closing time is later, then plunger governor motion 3-3 pilot plungers 3-2 rotation
Angle causes parts of the circumferential annular groove 3-2-1-1 away from axial straight trough 3-2-1-2 to be connected with oil leak hole 3-1-1, makes circumferential ring
Time that shape groove 3-2-1-1 is connected with oil leak hole 3-1-1 is shorter, oil leak hole 3-1-1 with circumferential annular groove 3-2-1-1 formation most
Small valid circulation area is smaller, causes the oil mass for flowing into energy storage chamber 9 in plunger oil pocket 3-5 and piston oil pocket 5-4 by oil leak hole
It is less, the maximum lift of valve has been reduced and has been closed after lower dead center, the curve B in such as Figure 10.Work as internal combustion engine
, it is necessary to which valve is fully opened when being run in high speed full load, and there is larger air inlet retard angle, then plunger governor motion 3-
3 by pilot plunger 3-2 rotational angle cause least significant ends of the circumferential annular groove 3-2-1-1 away from axial straight trough 3-2-1-2 with
Oil leak hole 3-1-1 is connected, or even circumferential annular groove 3-2-1-1 and oil leak hole 3-1-1 is disconnected all the time, plunger oil pocket 3-5 and work
The oil mass seldom even equal to 0 for flowing into energy storage chamber 9 in oil pocket 5-4 by oil leak hole 3-1-1 is filled in, now valve stroke depends on matching somebody with somebody
The molded line of gas cam, valve has the curve A in maximum lift and larger air inlet retard angle, such as Figure 10.
When valve-closing, if corresponding valve cam is still in the process of decline, with plunger 3-2 decline, post
When the pressure for filling in hydraulic oil in oil pocket 3-5 volume increase, high-pressure oil duct 1-1 decreases below the pressure of energy storage chamber 9, energy storage chamber
9 supplement hydraulic oil by inlet one-way valve 2 into high-pressure oil duct 1-1, it is ensured that hydraulic oil is full of plunger oil pocket 3-5, piston all the time
Oil pocket 5-4 and high-pressure oil duct 1-1.
To sum up, the utility model has the advantages that：
(1) the minimum valid circulation area that the oil leak hole on the circumferential annular groove and plunger bushing in plunger core is formed can be obtained
To accurate control, the time that circumferential annular groove 3-2-1-1 is connected with oil leak hole 3-1-1 can also accurately be adjusted, Neng Gouzhun
The oil mass that really control is flowed out from oil leak hole, makes valve maximum lift, valve duration angle and the continuous of close moment three can
Become.
(2) by the time for controlling circumference annular groove 3-2-1-1 to be connected with oil leak hole 3-1-1, and circumferential annular groove is adjusted
The size of the minimum valid circulation area of 3-2-1-1 and oil leak hole 3-1-1 formation, can accurately control hydraulic oil to flow out oil leak hole
3-1-1 flow velocity, is easy to accurately control valve stroke and its characteristics of motion, meets full hydraulic variable valve mechanism dynamic performance
Demand.
(3) put on full hydraulic variable valve mechanism valve stroke control device of the present utility model and camshaft, in put and
Underlying internal combustion engine all has good matching, using in traditional combustion engine, and the change of former machine is smaller and key components and parts
Without change.
(4) compared with external existing advanced technology, save high-frequency electromagnetic valve, thus with simple in construction, reliable operation,
Advantage with low cost,
(5) a set of valve stroke control device controls a cylinder, it is adaptable to single cylinder and multi-cylinder engine, expands and entirely may be used
Become the scope of application of hydraulic valve mechanism.
Described above is preferred embodiment of the present utility model, it is noted that for the ordinary skill of the art
For personnel, on the premise of principle described in the utility model is not departed from, some improvements and modifications can also be made, these improvement
Protection domain of the present utility model is also should be regarded as with retouching.
Claims (9)
1. a kind of full hydraulic variable valve mechanism valve stroke control device, it is characterised in that including being provided with high-pressure oil duct
Be provided with housing, the housing for be connected to Engine Cam drive component hydraulic plunger type oil-controlling device, for even
It is connected to the piston type pneumatic door drive of engine valve component, is filled for connecting the hydraulic energy-accumulating of I. C. engine oil lubricating system
Put and inlet one-way valve, wherein：
The hydraulic plunger type oil-controlling device includes setting plunger bushing on the housing, the endoporus matching with the plunger bushing
The plunger governor motion of the plunger of conjunction, the plunger spring for making the plunger return and the regulation plunger rotation angle, it is described
Plunger includes the plunger core being engaged with the plunger bushing and the plunger rod for being arranged at the plunger core lower end, the plunger core
Formed and be provided with the plunger oil pocket, the face of cylinder of the plunger core and the plunger oil pocket between top and the plunger bushing
Draining is provided with the axial straight trough of connection and the circumferential annular groove connected with the axial straight trough, the side wall of the plunger bushing
Hole；
The piston type pneumatic door drive includes hydraulic piston, the piston bush matched with hydraulic piston, the hydraulic piston
Top and the piston bush between form the piston oil pocket that is connected with the high-pressure oil duct；
The hydraulic accumulating device includes setting hydraulic accumulator on the housing and by the accumulator and the shell
The the first low pressure oil duct for connecting the energy storage chamber with oil leak hole is provided with the energy storage chamber that body is constituted, the housing, incites somebody to action described
The second low pressure oil duct that energy storage chamber is connected with high-pressure oil duct and by the energy storage chamber and the oil lubricating system connectivity of internal combustion engine
3rd low pressure oil duct, the energy storage chamber can by the first low pressure oil duct, oil leak hole, circumferential annular groove and axial straight trough with
The plunger oil pocket connection；
The inlet one-way valve is arranged between the high-pressure oil duct and the second low pressure oil duct.
2. full hydraulic variable valve mechanism valve stroke control device according to claim 1, it is characterised in that the week
Gradually increase or constant along plunger circumferencial direction since axial straight trough to distance of the top edge away from plunger top of annular groove, institute
The depth for stating circumferential annular groove is gradually reduced since axial straight trough along plunger circumferencial direction；
Or, distance of the top edge away from plunger top of the circumferential annular groove since axial straight trough along plunger circumferencial direction by
Cumulative big, the depth of the circumferential annular groove is constant.
3. full hydraulic variable valve mechanism valve stroke control device according to claim 2, it is characterised in that the week
It is not more than full depth from a quarter of the diameter of the oil leak hole to annular groove or partial depth.
4. full hydraulic variable valve mechanism valve stroke control device according to claim 3, it is characterised in that the week
It is triangle, circular arc, trapezoidal or rectangle to the cross section of annular groove.
5. according to any described full hydraulic variable valve mechanism valve stroke control device in Claims 1-4, its feature exists
In the plunger governor motion includes the control sleeve coordinated with the cylindrical gap in bottom of the plunger bushing, the control sleeve
End be provided with guide groove, the bottom of the plunger rod is provided with the joint tongue being engaged with the guide groove.
6. full hydraulic variable valve mechanism valve stroke control device according to claim 5, it is characterised in that the post
Fill in governor motion also include motor or proportion electro-magnet, the control sleeve it is cylindrical on be provided with gear ring, the motor or ratio
Example solenoid actuated is connected with the rack or gear being meshed with the gear ring.
7. according to any described full hydraulic variable valve mechanism valve stroke control device in Claims 1-4, its feature exists
In, the unidirectional hole connected respectively with the high-pressure oil duct and throttle orifice are provided with the piston type pneumatic door drive, it is described
Plunger shaft check valve is provided with unidirectional hole, the plunger shaft is connected by the unidirectional hole and throttle orifice with high-pressure oil duct, when
When valve assembly is closed, the top of the hydraulic piston is located at the top of the throttle orifice.
8. according to any described full hydraulic variable valve mechanism valve stroke control device in Claims 1-4, its feature exists
In the hydraulic accumulator includes being fixedly mounted end cap on the housing, the energy storage piston with body clearance cooperation
And it is arranged at the accumulator spring between the end cap and energy storage piston.
9. a kind of internal combustion engine, it is characterised in that including any described full hydraulic variable valve mechanism gas in claim 1 to 8
Door lift control.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201720149159.9U CN206530374U (en) | 2017-02-20 | 2017-02-20 | Full hydraulic variable valve mechanism valve stroke control device and internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201720149159.9U CN206530374U (en) | 2017-02-20 | 2017-02-20 | Full hydraulic variable valve mechanism valve stroke control device and internal combustion engine |
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| Publication Number | Publication Date |
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| CN206530374U true CN206530374U (en) | 2017-09-29 |
Family
ID=59916533
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|---|---|---|---|
| CN201720149159.9U Withdrawn - After Issue CN206530374U (en) | 2017-02-20 | 2017-02-20 | Full hydraulic variable valve mechanism valve stroke control device and internal combustion engine |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107060937A (en) * | 2017-02-20 | 2017-08-18 | 山东大学 | Full hydraulic variable valve mechanism valve stroke control device and internal combustion engine |
| CN108661744A (en) * | 2018-03-30 | 2018-10-16 | 潍柴动力股份有限公司 | A kind of engine intake valve continuously variable system and engine |
| CN116044538A (en) * | 2023-03-08 | 2023-05-02 | 龙口中宇热管理系统科技有限公司 | Hydraulic variable valve control mechanism |
-
2017
- 2017-02-20 CN CN201720149159.9U patent/CN206530374U/en not_active Withdrawn - After Issue
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107060937A (en) * | 2017-02-20 | 2017-08-18 | 山东大学 | Full hydraulic variable valve mechanism valve stroke control device and internal combustion engine |
| CN107060937B (en) * | 2017-02-20 | 2018-05-11 | 山东大学 | Full hydraulic variable valve mechanism valve stroke control device and internal combustion engine |
| WO2018149333A1 (en) * | 2017-02-20 | 2018-08-23 | 山东大学 | Valve lift control device of hydraulic fully variable valve mechanism and internal combustion engine |
| CN108661744A (en) * | 2018-03-30 | 2018-10-16 | 潍柴动力股份有限公司 | A kind of engine intake valve continuously variable system and engine |
| CN116044538A (en) * | 2023-03-08 | 2023-05-02 | 龙口中宇热管理系统科技有限公司 | Hydraulic variable valve control mechanism |
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| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| EE01 | Entry into force of recordation of patent licensing contract | ||
| EE01 | Entry into force of recordation of patent licensing contract |
Assignee: Longkou Zhongyu Heat Management System Technology Co., Ltd. Assignor: Shandong University Contract record no.: 2017370010009 Denomination of utility model: Valve lift control device of fully variable hydraulic valve mechanism and internal combustion engine Granted publication date: 20170929 License type: Exclusive License Record date: 20171212 |
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| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20170929 Effective date of abandoning: 20180511 |
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| AV01 | Patent right actively abandoned |
Granted publication date: 20170929 Effective date of abandoning: 20180511 |